JPS591813A - Clutch disc - Google Patents

Abstract

PURPOSE:To enable effective vibro-absorption and friction damping throughout the operating range by selectively operating a low-friction force damping means for a low torsional rigidity and a high-friction force damping means for a high torsional rigidity according to variation of input torque. CONSTITUTION:Until the raised tips 18 of each of forked members 15 and 16 come into contact with the window 11 of a plate part 3 of a hub 1, the forked members 15 and 16 are integral with drive plates 5 and 5' so that they are turned under the influence of the efforts of the first friction damping means 20 and 21, repsectively. On and after the contacting, the forked members 15 and 16 are integral with the plate part 3 of the hub 1 so that they are turned under the influence of the efforts of the second friction damping means 22 and 23, respectively. The driving torque of an engine may be smoothly transmitted according to both the torsional rigidity which is variously changed and the intense of input torque, hence effectively absorbing vibration and noise of the entire power transmission system of automobiles or the like throughout the operation range.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a latch disk used in an automobile power transmission device or the like.

In order to effectively absorb torsional vibrations generated from the engine, etc., and prevent undesirable vibrations or noise from occurring in the power transmission system, clutch discs are designed with an arc-shaped (compression spring acting on this and a friction damping element attached to it). It is well known to apply a vibration damping device consisting of means. Such a clutch disc vibration damping device absorbs torsional vibrations and noise generated in the power transmission system 1, and in order to ensure sufficient torque transmission. For small input torque ranges, it is desirable to reduce torsional rigidity and increase displacement to increase the vibration absorption effect, and for large torques, it is desirable to have characteristics that allow sufficient torque transmission with high rigidity, and at the same time, to reduce friction. It is also desired that the damping capacity of the damping means changes in proportion to its torque.

For conventional clutch discs, attempts have been made to gradually change the torsional rigidity due to compression spring according to the magnitude of human torque, but it has not been possible to effectively Friction damping means for damping rotational vibrations have not yet achieved sufficient friction damping characteristics due to problems such as the spraying method and selection of friction materials.

The present invention has been made in view of the above-mentioned circumstances, and it applies a friction damping means with a small frictional force when the torsional rigidity is small and a friction damping means with a large frictional force when the torsional rigidity is large according to the fluctuation of the input torque. It is an object of the present invention to provide a clutch disc that can effectively absorb and damp vibration over the entire range of operation when operated.

Embodiments of the present invention will be described in detail below with reference to the drawings.

FIG. 1 is a stop view of a clutch disk showing an embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along the line -] in FIG. In addition, in FIG. 1, a portion of the drive plate is shown cut away for convenience of explanation.

In the figure, I denotes a hub consisting of a boss part 2 and a plate part 3, and the boss part 2 has a spline q carved therein for connection to an output shaft (not shown). Reference numerals 5 and 5' denote a pair of drive plates facing each other on both sides of the plate section 3 of the front H[: hub I. A plurality of compression springs are arranged with different characteristics in order to connect them in a phantom rotational manner.Here, 6 is the first of the multi-stage characteristics.
a compression spring acting in stages, the compression spring 6 having the same width in the circumferential direction;
Preferably, it is accommodated with the desired initial cart. 9
is the compression spring that acts on the second stage, and is this compression spring 9 the initial stage? Three windows with tiDA are arranged at intervals on the upper collar of the circumference, and the width in the circumferential direction of the window IO provided in the plate part 3 of the hub I among the windows accommodating each of these windows is 1'U, The drive plate 5.5' is formed with larger dimensions than the window 11 provided in the drive plate 5.5'. Further, L2 is a compression spring that acts on the third stage, and each of the compression springs 12 has a dimensional difference larger than the circumferential dimensional difference between the windows 10 and 11 that accommodate each of the compression springs 9. It is housed within the windows 13 and 14.

Fork members 15 and 16 are interposed between at least one of the drive plates 5 and 5' and the plate portion 3 of the knob I, respectively, in this embodiment both. These fork members 15 and 16 are formed into a ring shape as shown in FIG. At the periphery, the drive plate s,
With the same width as the circumferential width of the window 11 formed at s',
engaging the compression spring 9 housed within the window 11 without any play 7;
A pair of fork portions 19 are provided in a protruding manner, and each of the fork portions 19 has a pair of protruding tongues 18 on opposite sides thereof, which engage with the window 10 of the hub I at a desired angle of play.

Reference numerals 20 and 21 designate friction/yeon wheels which are first friction damping means disposed between the plate portion 3 of the hub 1 and the fork members 15 and 16, respectively.

Further, 22 and 23 are second friction damping means disposed between the fork member 15 and the drive plate 5 and between the fork member 16 and the drive plate 5', respectively. The wheels 22 and 23 have a coefficient of friction larger than that of the friction damping means 20 and 21 of the front brake 1. 24 is a claw piece 24 on one end side
a retainer plate disposed between the fork part I/I 15 and the fork part I/I 15 with the retainer plate held in the small window 15 a of the fork part IJ 115 without any play;
Reference numeral 25 denotes a disc spring disposed between the front 8-friction plate 24 and the fork part support 5, and the spring force of the slope spring 25 causes the above-mentioned friction/yeonwatsunoya.23 indicates the drive plate 5 via the retainer plate 24. It is pressed against the inner surface of ゜5'. Note that 5 is a pair of fork members 15, 1
6, l is a rivet that integrally connects the pair of drive plates 5 and s', and ff is a main friction plate fixed to one of the drive plates 5.

In such a configuration, when engine torque is transmitted to the clutch disc, one drive plate 5 to which the main friction plate y is attached tends to rotate together with the other drive plate 5', causing compression springs 6, . 9, 12 to 10
The torque is transmitted to the hub I through 00-order compression.

At this time, when the drive plates s, s' to the plate portion 3 of the hub I are rotated, the spring force of the compression spring 6 (against this, the friction washers 20, 21, which are the first friction damping means) is rotated. The window 10 of the plate portion 3 of the hub I is exposed to the frictional resistance caused by the fork member 15.
, rotates until it comes into contact with the upright tongue piece 18 of I6, and a vibration absorbing and damping action of the '@1 stage (area A) shown in FIG. 4 occurs.

When the drive plate 5.5' and the plate part 3 of the hub I are further rotated, the plate part 3 of the hub I is rotated through the window 10.
are abuttingly engaged with the upright tongue piece 18, so the hub I-shaped fork members 15 and I6 are integrated, and the hub 1 rotates together with these fork members 15 and 16. Thus, the drive plate 5.5' receives frictional resistance from the friction washers 23, which are second friction damping means having a larger coefficient of friction than the friction washers 20 and 21, and receives the compression spring in addition to the compression spring 6. The second stage of vibration absorption and damping action is produced by Kokichi compressing 9 (Fig. (Region C in Figure 4).

Thus, in the small human torque range, the friction wheels 20 and 21, which have relatively small IJQ coefficients, act as a shift, and in the large torque range, the above-mentioned 7 riku/yo/watu/ya 20
, 21 have a coefficient of friction larger than f, V, the friction damping ability is changed according to the magnitude of the input torque, and vibration noise is effectively reduced. 'I can.

Here, the second friction damping means 22, 2.9, which acts in a large torque range, is pressed against its working surface by the disc spring 25 with a repelling force. The friction damping capacity of the coil 1 can be greatly increased.Furthermore, since the fork members 15 and 16 are engaged with the compression spring 9 without any play, when the torsional torque is removed, the fork members ts and 16 can be reliably returned to its initial position, and the above-mentioned vibration absorption and damping effect is advantageous in that it has the same effect on vibrations in both the forward and reverse directions.

Note that the retainer plate 24 and the disc spring 25 change the axial length of the rivet 22 and the rivet y, thereby changing the distance between the fork members 15 and 16 that are connected together and the width of the drive plate 5.5'. This can be abolished by controlling the distance between them. Also, fork member t5. Either one of te may be a circular annular plate.

As described above, according to the present invention, a hub having a plate portion and a pair of drive plates facing each other on both sides of the plate portion are elastically moved relative to each other by compression springs accommodated in a plurality of windows formed therein. In order to obtain multi-stage elasticity, at least one of the windows provided in the drive plate is larger in the circumferential direction than the window in the drive plate corresponding to the drive plate. In the clutch disc formed therein, the drive plate (the drive plate (the drive plate) is housed in the window and has the same width as the circumferential width of the window formed between at least one of the drive plates and the plate portion of the hub. A fork member having an upright tongue that engages the IE compression spring without play and engages the window of the plate portion of the hub with a desired angle of play, and between the plate portion of the hub and the fork member. 1st
A PM friction damping means is attached between the fork member and the drive plate, and a second friction damping means is attached between the fork member and the drive plate. Since the fork member is raised so that the fork member is in contact with the window in the plate portion of the hub, the fork member becomes integral with the drive plate until the upright tongue comes into contact with the window in the plate portion of the hub, and the drive plate is in contact with the first friction damping means. After that, the fork member becomes integral with the plate part of the hub and rotates under the action of the second friction damping means, so the torsional rigidity changes in multiple stages and the magnitude of the human torque. The engine's driving torque can be transmitted to the internal engine with a friction damping capacity corresponding to the engine speed. It effectively absorbs the vibrations and Iv6'i of the entire power transmission system of automobiles etc. over the entire range of operation, making it a smart 1. A clutch disc with superior power transmission performance can be obtained.

[Brief explanation of the drawing]

Fig. 1 is a front view showing the clutch disc of the present invention with a part of the drive plate cut away, and Fig. 2 is the -
3 is a partially cutaway perspective view of the phase of the fork portion, and FIG. 4 is a torsional characteristic diagram. 1...Hub, 3...Plate part s, , c, l
Drive plate, 6, 9, 12 ・Compression spring,
7, 8, 10. 11, 13, 14...window, Il'i, +6
Fork member, 18... Upright tongue piece, 19. Fork portion, 21, 21... First friction damping means (flick 7 yonwa/ya), 22, 2.9... Second friction damping means (flick /Yonwa/Ya). Figure 2 Figure 3 Figure 4

Claims (1)

Scope of Claims (11) A hub having a plate portion and a pair of drive plates facing each other on both sides of this plate portion,
The compression springs accommodated in the plurality of windows formed in this manner are coupled to the elastic member so as to be rotatable relative to each other, and in order to obtain multi-stage elasticity, at least one of the windows provided in the hub includes: In a clutch disk formed to be larger in the circumferential direction than a window in a corresponding drive plate, a window is formed in the drive plate between at least one of the drive plates and a plate portion of the hub. a fork member having an upright tongue that engages the compression spring housed in the window without any play and has a width equal to the circumferential width of the fork member and that engages the window of the plate portion of the hub at a desired angle of play; , a first friction damping means is attached between the plate portion of the hub and the fork member, and a second friction damping means is attached between the fork member and the drive plate.
A clutch disc characterized in that it is provided with friction damping means, and the activation of at least one friction damping means is controlled by the fork member. (2) The clutch disc according to claim 1, wherein the friction coefficient of the first friction damping means is smaller than the friction coefficient of the second friction damping means.